CA2743809C - Flexible shaft wind turbine - Google Patents
Flexible shaft wind turbine Download PDFInfo
- Publication number
- CA2743809C CA2743809C CA2743809A CA2743809A CA2743809C CA 2743809 C CA2743809 C CA 2743809C CA 2743809 A CA2743809 A CA 2743809A CA 2743809 A CA2743809 A CA 2743809A CA 2743809 C CA2743809 C CA 2743809C
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- Canada
- Prior art keywords
- shaft
- hub
- wind turbine
- main frame
- drive shaft
- Prior art date
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- Expired - Fee Related
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03D—WIND MOTORS
- F03D15/00—Transmission of mechanical power
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C3/00—Shafts; Axles; Cranks; Eccentrics
- F16C3/02—Shafts; Axles
- F16C3/026—Shafts made of fibre reinforced resin
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03D—WIND MOTORS
- F03D15/00—Transmission of mechanical power
- F03D15/20—Gearless transmission, i.e. direct-drive
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03D—WIND MOTORS
- F03D80/00—Details, components or accessories not provided for in groups F03D1/00 - F03D17/00
- F03D80/70—Bearing or lubricating arrangements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03D—WIND MOTORS
- F03D80/00—Details, components or accessories not provided for in groups F03D1/00 - F03D17/00
- F03D80/80—Arrangement of components within nacelles or towers
- F03D80/88—Arrangement of components within nacelles or towers of mechanical components
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03D—WIND MOTORS
- F03D80/00—Details, components or accessories not provided for in groups F03D1/00 - F03D17/00
- F03D80/30—Lightning protection
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2240/00—Components
- F05B2240/10—Stators
- F05B2240/14—Casings, housings, nacelles, gondels or the like, protecting or supporting assemblies there within
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2240/00—Components
- F05B2240/50—Bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2240/00—Components
- F05B2240/60—Shafts
- F05B2240/62—Shafts flexible
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2260/00—Function
- F05B2260/96—Preventing, counteracting or reducing vibration or noise
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2280/00—Materials; Properties thereof
- F05B2280/60—Properties or characteristics given to material by treatment or manufacturing
- F05B2280/6003—Composites; e.g. fibre-reinforced
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
- F05C2253/00—Other material characteristics; Treatment of material
- F05C2253/04—Composite, e.g. fibre-reinforced
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2360/00—Engines or pumps
- F16C2360/31—Wind motors
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E10/00—Energy generation through renewable energy sources
- Y02E10/70—Wind energy
- Y02E10/72—Wind turbines with rotation axis in wind direction
Abstract
A horizontal-axis wind turbine is described, the wind turbine of a rotor- support de-sign, wherein the structural load of the wind turbine rotor is carried by the wind tur-bine tower itself. The turbine uses a composite shaft to transfer torque from the wind turbine rotor to the generator, the shaft having high torsional strength but being flexi-ble in bending. This prevents the transmission of bending moments from the rotor hub to the generator system. Accordingly, the components of the turbine can be rigidly mounted to the turbine main frame, removing the need for vibration damping ele-ments. The result is a wind turbine of reduced weight, which can be modelled and de-signed for improved efficiency and performance. Furthermore, as the turbine compo-nents do not have to be load-balanced, the turbine can be of a modular construction for relatively easy servicing and/or upgrading.
Description
Flexible Shaft Wind Turbine Field of the Invention The present invention relates to a wind turbine, in particular to a wind turbine having the wind turbine hub supported directly by the main frame, such that the transmission of torque from the hub to the generator is separated from the support of the rotor.
Background of the Invention Rotor support-type wind turbines are a known alternative wind turbine design, wherein the structural load of the hub and rotor blades is provided by a fixed support shaft provided on the wind turbine main frame. As the hub is allowed to rotate freely about the support shaft, consequentially the structural load is transferred to the main frame while the torque provided by the spinning rotor blades is transferred to the gen-eration system.
US 4,757,211 discloses a rotor support-type wind turbine wherein a rotor hub is mounted onto a cylindrical section of the machine housing, the structural load of the rotor hub being supported by the machine housing. A hub shaft extends from the hub to the gearbox, and is accordingly coupled to the generator.
One of the disadvantages of such a system is that in order to compensate for vibrations and bending moments transferred through the hub shaft from the hub, the generator and the gearbox must be mounted on vibration damping elements which are coupled to the machine housing. Furthermore, the hub is mounted to the machine housing util-ising flexible bushings and further damping elements. Damping elements can also used in such constructions to compensate for misalignments between turbine compo-nents, e.g. in the case of the hub shaft and the gearbox not being perfectly aligned.
Such damping elements are subject to wear and tear during the lifetime of the system, often requiring replacement every 3-5 years in a relatively costly maintenance opera-tion, at which time the turbine must be taken out of service for an extended period of time.
Background of the Invention Rotor support-type wind turbines are a known alternative wind turbine design, wherein the structural load of the hub and rotor blades is provided by a fixed support shaft provided on the wind turbine main frame. As the hub is allowed to rotate freely about the support shaft, consequentially the structural load is transferred to the main frame while the torque provided by the spinning rotor blades is transferred to the gen-eration system.
US 4,757,211 discloses a rotor support-type wind turbine wherein a rotor hub is mounted onto a cylindrical section of the machine housing, the structural load of the rotor hub being supported by the machine housing. A hub shaft extends from the hub to the gearbox, and is accordingly coupled to the generator.
One of the disadvantages of such a system is that in order to compensate for vibrations and bending moments transferred through the hub shaft from the hub, the generator and the gearbox must be mounted on vibration damping elements which are coupled to the machine housing. Furthermore, the hub is mounted to the machine housing util-ising flexible bushings and further damping elements. Damping elements can also used in such constructions to compensate for misalignments between turbine compo-nents, e.g. in the case of the hub shaft and the gearbox not being perfectly aligned.
Such damping elements are subject to wear and tear during the lifetime of the system, often requiring replacement every 3-5 years in a relatively costly maintenance opera-tion, at which time the turbine must be taken out of service for an extended period of time.
2 Additionally, the presence of dampers in the turbine system introduces a variable ele-ment to turbine modelling, in that it can be hard to predict where the most stresses on the other turbine components will occur, due to the unpredictability of the perform-ance of the damper elements.
Object of the Invention It is an object of the invention to provide a wind turbine design having improved reli-ability, ease of servicing, and is easier to model at the initial design stage.
Description of the Invention Accordingly, in some embodiments there is provided a horizontal-axis wind turbine having a rotor with a diameter of at least 50m length, the turbine comprising:
a wind turbine main frame;
a generator system, at least a portion of which is rigidly mounted to said main frame;
a rotor hub, said hub mounted to a rigid support shaft provided on said main frame, wherein said hub is operable to rotate about said support shaft and wherein said support shaft transfers the structural load of said hub to said main frame, and a drive shaft rigidly connected to and extending from said hub, wherein said drive shaft is connected to said generator system to transfer torque from said hub to said generator system, and wherein said drive shaft is a mechanically anisotropic shaft adapted to limit the bending moments transferred between said hub and said generator system.
In some embodiments, there is provided a horizontal-axis wind turbine having a rotor with a diameter of at least 50m length, the turbine comprising:
a main frame;
a generator system, at least a portion of which is rigidly mounted to said main frame;
a rotor hub, said hub mounted to a rigid support shaft provided on said main frame, wherein said rotor hub is operable to rotate about said rigid support shaft and wherein said rigid support shaft is configured to transfer a structural load of said rotor hub to said main frame; and 2a a drive shaft rigidly connected to and extending from said rotor hub, wherein said drive shaft is connected to said generator system and configured to transfer torque from said rotor hub to said generator system, wherein said drive shaft is a mechanically anisotropic shaft adapted to limit bending moments transferred between said rotor hub and said generator system.
According to another aspect of the present invention, there is provided a horizontal-axis wind turbine having a rotor with a diameter of at least 50 m length, the turbine comprising:
a wind turbine main frame;
a generator system comprising a generator that is rigidly mounted to said main frame without vibration damping elements;
a rotor hub, said hub mounted to a rigid support shaft provided on said main frame, wherein said hub is operable to rotate about said support shaft and wherein said support shaft transfers structural loading of said hub to said main frame; and a drive shaft rigidly connected to and extending from said hub, wherein said drive shaft is connected to said generator system to transfer torque from said hub to said generator system, wherein said drive shaft is a mechanically anisotropic shaft that has sufficient flexibility for preventing transmission of bending moments from the hub to the generator system by absorption of the bending moments;
wherein the drive shaft comprises a first coupling flange at its first end and a second coupling flange at an opposite end, the first coupling flange being bolted to said rotor hub and the second coupling flange being bolted to said generator system;
wherein the drive shaft is only supported at said first and second coupling flanges by said hub and said generator system, the drive shaft being free of shaft bearings and rollers at locations between the first and second ends.
According to another aspect of the present invention, there is provided a horizontal-axis wind turbine having a rotor with a diameter of at least 50 m length, the turbine comprising:
a wind turbine main frame;
2b a generator system at least a portion of which is rigidly mounted to said main frame;
a rotor hub, said hub mounted to a rigid support shaft provided on said main frame, wherein said hub is operable to rotate about said support shaft and wherein said support shaft transfers structural loading of said hub to said main frame; and a drive shaft rigidly connected to and extending from said hub, wherein said drive shaft is connected to said generator system to transfer torque from said hub to said generator system, wherein said drive shaft is a mechanically anisotropic shaft adapted to limit the bending moments transferred between said hub and said generator system, wherein said shaft comprises a fiber composite main shaft body and at least one coupling flange formed from a rigid material suitable for bolting, said at least one coupling flange being arranged to couple with at least one end of said main shaft body, wherein said at least one end of said fiber composite main shaft body is outwardly flared, and wherein said at least one coupling flange comprises a first substantially frustoconical projection, said first substantially frustoconical projection of said at least one coupling flange being received within said at least one outwardly flared end of said main shaft body.
Such a construction allows for the structural load of the rotor to be carried by the tur-bine main frame. As the drive shaft is anisotropic, this means it has different mechani-cal properties in different directions ¨ the shaft is flexible with regard to bending mo-ments, and high in torsional strength. Accordingly, the drive shaft is able to transfer torque from the rotor hub to the generator, but is able to deflect to prevent the trans-mission of bending moments from the hub to the generator, i.e. the shaft is operable to absorb the bending moments from the rotor hub. As a result, a portion or all of the generator system may be rigidly mounted to the main frame of the wind turbine, which may remove the need for damping elements to protect the generator system.
Object of the Invention It is an object of the invention to provide a wind turbine design having improved reli-ability, ease of servicing, and is easier to model at the initial design stage.
Description of the Invention Accordingly, in some embodiments there is provided a horizontal-axis wind turbine having a rotor with a diameter of at least 50m length, the turbine comprising:
a wind turbine main frame;
a generator system, at least a portion of which is rigidly mounted to said main frame;
a rotor hub, said hub mounted to a rigid support shaft provided on said main frame, wherein said hub is operable to rotate about said support shaft and wherein said support shaft transfers the structural load of said hub to said main frame, and a drive shaft rigidly connected to and extending from said hub, wherein said drive shaft is connected to said generator system to transfer torque from said hub to said generator system, and wherein said drive shaft is a mechanically anisotropic shaft adapted to limit the bending moments transferred between said hub and said generator system.
In some embodiments, there is provided a horizontal-axis wind turbine having a rotor with a diameter of at least 50m length, the turbine comprising:
a main frame;
a generator system, at least a portion of which is rigidly mounted to said main frame;
a rotor hub, said hub mounted to a rigid support shaft provided on said main frame, wherein said rotor hub is operable to rotate about said rigid support shaft and wherein said rigid support shaft is configured to transfer a structural load of said rotor hub to said main frame; and 2a a drive shaft rigidly connected to and extending from said rotor hub, wherein said drive shaft is connected to said generator system and configured to transfer torque from said rotor hub to said generator system, wherein said drive shaft is a mechanically anisotropic shaft adapted to limit bending moments transferred between said rotor hub and said generator system.
According to another aspect of the present invention, there is provided a horizontal-axis wind turbine having a rotor with a diameter of at least 50 m length, the turbine comprising:
a wind turbine main frame;
a generator system comprising a generator that is rigidly mounted to said main frame without vibration damping elements;
a rotor hub, said hub mounted to a rigid support shaft provided on said main frame, wherein said hub is operable to rotate about said support shaft and wherein said support shaft transfers structural loading of said hub to said main frame; and a drive shaft rigidly connected to and extending from said hub, wherein said drive shaft is connected to said generator system to transfer torque from said hub to said generator system, wherein said drive shaft is a mechanically anisotropic shaft that has sufficient flexibility for preventing transmission of bending moments from the hub to the generator system by absorption of the bending moments;
wherein the drive shaft comprises a first coupling flange at its first end and a second coupling flange at an opposite end, the first coupling flange being bolted to said rotor hub and the second coupling flange being bolted to said generator system;
wherein the drive shaft is only supported at said first and second coupling flanges by said hub and said generator system, the drive shaft being free of shaft bearings and rollers at locations between the first and second ends.
According to another aspect of the present invention, there is provided a horizontal-axis wind turbine having a rotor with a diameter of at least 50 m length, the turbine comprising:
a wind turbine main frame;
2b a generator system at least a portion of which is rigidly mounted to said main frame;
a rotor hub, said hub mounted to a rigid support shaft provided on said main frame, wherein said hub is operable to rotate about said support shaft and wherein said support shaft transfers structural loading of said hub to said main frame; and a drive shaft rigidly connected to and extending from said hub, wherein said drive shaft is connected to said generator system to transfer torque from said hub to said generator system, wherein said drive shaft is a mechanically anisotropic shaft adapted to limit the bending moments transferred between said hub and said generator system, wherein said shaft comprises a fiber composite main shaft body and at least one coupling flange formed from a rigid material suitable for bolting, said at least one coupling flange being arranged to couple with at least one end of said main shaft body, wherein said at least one end of said fiber composite main shaft body is outwardly flared, and wherein said at least one coupling flange comprises a first substantially frustoconical projection, said first substantially frustoconical projection of said at least one coupling flange being received within said at least one outwardly flared end of said main shaft body.
Such a construction allows for the structural load of the rotor to be carried by the tur-bine main frame. As the drive shaft is anisotropic, this means it has different mechani-cal properties in different directions ¨ the shaft is flexible with regard to bending mo-ments, and high in torsional strength. Accordingly, the drive shaft is able to transfer torque from the rotor hub to the generator, but is able to deflect to prevent the trans-mission of bending moments from the hub to the generator, i.e. the shaft is operable to absorb the bending moments from the rotor hub. As a result, a portion or all of the generator system may be rigidly mounted to the main frame of the wind turbine, which may remove the need for damping elements to protect the generator system.
3 Preferably, said drive shaft is rigidly connected to said generator system.
It will be understood that the use of the term "rigidly mounted" means that compo-nents are fixed without the use of damping elements, i.e. the components are not flexi-bly mounted in the wind turbine structure, e.g. without the use of rubber mounts, dampers, torque arms, etc.
It will be understood that the use of the term "rigidly connected" means that compo-nents are directly connected or mounted together, e.g. without damping elements and/or without relative motion between the connected components.
As the shaft used is flexible to absorb the transmission of vibrations between the rotor and the generator system, such rigid mounting and connecting of components can be accomplished, which may eliminate the need for vibration damping elements in the wind turbine construction.
Preferably, the entire generator system is rigidly mounted to the main frame of the wind turbine, eliminating the need for any vibration damping elements in the system.
Preferably, said drive shaft is a composite material shaft.
Preferably, the drive shaft is selected from one of the following: a filament wound shaft, a pre-preg fibre composite shaft, a slatted-construction shaft. Fibres in such a shaft can be chosen among several types of fibres e.g. glass, carbon, basalt, aramid, organic fibres.
Preferably, said generator system comprises a gearbox coupled to a generator, said gearbox rigidly mounted to said main frame, wherein said drive shaft is directly con-nected to said gearbox to drive said generator.
The generator may also be rigidly mounted to said main frame in this construction.
It will be understood that the use of the term "rigidly mounted" means that compo-nents are fixed without the use of damping elements, i.e. the components are not flexi-bly mounted in the wind turbine structure, e.g. without the use of rubber mounts, dampers, torque arms, etc.
It will be understood that the use of the term "rigidly connected" means that compo-nents are directly connected or mounted together, e.g. without damping elements and/or without relative motion between the connected components.
As the shaft used is flexible to absorb the transmission of vibrations between the rotor and the generator system, such rigid mounting and connecting of components can be accomplished, which may eliminate the need for vibration damping elements in the wind turbine construction.
Preferably, the entire generator system is rigidly mounted to the main frame of the wind turbine, eliminating the need for any vibration damping elements in the system.
Preferably, said drive shaft is a composite material shaft.
Preferably, the drive shaft is selected from one of the following: a filament wound shaft, a pre-preg fibre composite shaft, a slatted-construction shaft. Fibres in such a shaft can be chosen among several types of fibres e.g. glass, carbon, basalt, aramid, organic fibres.
Preferably, said generator system comprises a gearbox coupled to a generator, said gearbox rigidly mounted to said main frame, wherein said drive shaft is directly con-nected to said gearbox to drive said generator.
The generator may also be rigidly mounted to said main frame in this construction.
4 Alternatively, said generator system comprises a generator rigidly mounted to said main frame, and wherein said drive shaft is directly connected to said generator.
As the components can be rigidly mounted to the main frame, there may be no need to use vibration damping elements for the components of the generator system. As damping elements are not used, damper failure may cease to be an issue for the design of the.
turbine. Accordingly, loads experienced by the turbine components may be more easily predicted and modelled, with the result that turbine structure may be optimised at the design stage.
Preferably, said rigid support shaft is provided at a first end of said main frame, and wherein said generator system is releasably mounted to a second opposed end of said main frame.
Preferably, said generator system is releasably mounted to an exterior surface of said main frame.
As the drive shaft is flexible enough to prevent transmission of bending moments from the hub to the generator system, the components do not have to be load-wise mounted within the turbine. Accordingly, as the components of the turbine are releasably mounted to the main frame, this may provide for modular construction of the turbine, and may provide for easy servicing of installed turbines ¨ components may be easily re-moved and replaced without complicated mounting/de-mounting operations. It will be understood that this releasable mounting may be rigidly mounted, i.e. without the use of damping elements.
Preferably, said rigid support shaft is releasably mounted to said first end of said main frame.
Preferably, the wind turbine comprises at least two sets of hub bearings provided at said support shaft, said hub mounted to said sets of hub bearings.
As the components can be rigidly mounted to the main frame, there may be no need to use vibration damping elements for the components of the generator system. As damping elements are not used, damper failure may cease to be an issue for the design of the.
turbine. Accordingly, loads experienced by the turbine components may be more easily predicted and modelled, with the result that turbine structure may be optimised at the design stage.
Preferably, said rigid support shaft is provided at a first end of said main frame, and wherein said generator system is releasably mounted to a second opposed end of said main frame.
Preferably, said generator system is releasably mounted to an exterior surface of said main frame.
As the drive shaft is flexible enough to prevent transmission of bending moments from the hub to the generator system, the components do not have to be load-wise mounted within the turbine. Accordingly, as the components of the turbine are releasably mounted to the main frame, this may provide for modular construction of the turbine, and may provide for easy servicing of installed turbines ¨ components may be easily re-moved and replaced without complicated mounting/de-mounting operations. It will be understood that this releasable mounting may be rigidly mounted, i.e. without the use of damping elements.
Preferably, said rigid support shaft is releasably mounted to said first end of said main frame.
Preferably, the wind turbine comprises at least two sets of hub bearings provided at said support shaft, said hub mounted to said sets of hub bearings.
5 Preferably, said drive shaft is directly connected between said hub and said generator system.
As the drive shaft extends from the hub, with the structural load of the rotor hub car-ried by the rigid support shaft and the main frame, there may be no need for any support of the drive shaft in the turbine.
Preferably, the drive shaft is a hollow shaft.
Preferably, the wall thickness of the drive shaft is chosen to be any suitable dimension between 10mm-400mm.
Preferably, the drive shaft comprises a nanocomposite material. This may include nano clay, carbon nano tubes, nano silica.
Preferably, the drive shaft is made from an electrically insulating material.
This pre-vents the transmission of current in the event of a lightening strike, which may damage wind turbine components.
Preferably, the drive shaft is at least 3m in length. Further preferably, the drive shaft is at least 7 metres in length. Preferably, the drive shaft comprises an outer diameter of at least 1 metre.
Preferably, the turbine has a maximum power rating of at least 2MW.
Preferably, said shaft comprises a fibre composite main shaft body and at least one coupling flange formed from a rigid material suitable for bolting, said at least one cou-pling flange arranged to couple with at least one end of said main shaft body.
As the coupling flange may be formed from a material different to the fibre-based ma-terial of the main shaft body, this means that a more secure bolting connection may be established between the drive shaft and the other wind turbine components.
Preferably the coupling flange is formed from a metallic material, e.g. steel.
As the drive shaft extends from the hub, with the structural load of the rotor hub car-ried by the rigid support shaft and the main frame, there may be no need for any support of the drive shaft in the turbine.
Preferably, the drive shaft is a hollow shaft.
Preferably, the wall thickness of the drive shaft is chosen to be any suitable dimension between 10mm-400mm.
Preferably, the drive shaft comprises a nanocomposite material. This may include nano clay, carbon nano tubes, nano silica.
Preferably, the drive shaft is made from an electrically insulating material.
This pre-vents the transmission of current in the event of a lightening strike, which may damage wind turbine components.
Preferably, the drive shaft is at least 3m in length. Further preferably, the drive shaft is at least 7 metres in length. Preferably, the drive shaft comprises an outer diameter of at least 1 metre.
Preferably, the turbine has a maximum power rating of at least 2MW.
Preferably, said shaft comprises a fibre composite main shaft body and at least one coupling flange formed from a rigid material suitable for bolting, said at least one cou-pling flange arranged to couple with at least one end of said main shaft body.
As the coupling flange may be formed from a material different to the fibre-based ma-terial of the main shaft body, this means that a more secure bolting connection may be established between the drive shaft and the other wind turbine components.
Preferably the coupling flange is formed from a metallic material, e.g. steel.
6 Preferably, said at least one end of said fibre composite main body is outwardly flared, and wherein said at least one coupling flange comprises a first substantially frusto-conical projection, said first frustoconical projection of said at least one coupling flange received within said at least one flared end of said main shaft body.
Providing a flared end of the main shaft body may allow for an easy insertion of the cou-pling flange into the interior of the main shaft body. Such a structure is relatively eas-ily fabricated during curing of a fibre-based shaft.
Preferably, said shaft comprises a plurality of pins extending between said at least one flared end of said man shaft body and said first frustoconical projection of said at least one coupling flange, said plurality of pins retaining said at least one coupling flange within said at least one flared end of said man shaft body.
The use of a series of pins, preferably arranged in a series of parallel rows along the interior of the flared section, allows for the fibre-based main shaft body to be securely coupled to the coupling flange, acting to bolt the coupling flanges securely to the main shaft body.
Preferably, said shaft is arranged such that a portion of fibres at said at least one flared end are wound around said plurality of pins to provide for an equal distribution of forces between said at least one coupling flange and said shaft body, and to improve retention of said pins in the shaft body.
The fibres may be oriented at the flared section to wind around or be intertwined with the pins at the flared section, providing for an improved coupling and retention of the pins within the main shaft body. Alternatively, holes may be formed, e.g. by drilling, in the at least one flared end of said main shaft body, said holes arranged to receive a plurality of pins extending from said first frustoconical projection of said at least one coupling flange into said at least one flared end of said man shaft body.
Providing a flared end of the main shaft body may allow for an easy insertion of the cou-pling flange into the interior of the main shaft body. Such a structure is relatively eas-ily fabricated during curing of a fibre-based shaft.
Preferably, said shaft comprises a plurality of pins extending between said at least one flared end of said man shaft body and said first frustoconical projection of said at least one coupling flange, said plurality of pins retaining said at least one coupling flange within said at least one flared end of said man shaft body.
The use of a series of pins, preferably arranged in a series of parallel rows along the interior of the flared section, allows for the fibre-based main shaft body to be securely coupled to the coupling flange, acting to bolt the coupling flanges securely to the main shaft body.
Preferably, said shaft is arranged such that a portion of fibres at said at least one flared end are wound around said plurality of pins to provide for an equal distribution of forces between said at least one coupling flange and said shaft body, and to improve retention of said pins in the shaft body.
The fibres may be oriented at the flared section to wind around or be intertwined with the pins at the flared section, providing for an improved coupling and retention of the pins within the main shaft body. Alternatively, holes may be formed, e.g. by drilling, in the at least one flared end of said main shaft body, said holes arranged to receive a plurality of pins extending from said first frustoconical projection of said at least one coupling flange into said at least one flared end of said man shaft body.
7 Preferably, a coupling flange is provided at either end of the main shaft body. Prefera-bly, a first coupling flange is bolted to said rotor hub and a second coupling flange is bolted to said generator system.
Preferably, the drive shaft comprises a composite fibre shaft, wherein substantially all of the fibres are oriented in a parallel winding direction. Preferably, at least 50% to 95% of the fibres are oriented in a parallel winding direction.
As the fibres are oriented in the same direction, the torsional strength will be concen-trated in that direction. As in wind turbines the drive shaft will only rotate in one di-rection, consequently substantially all of the torque will only ever be transferred to the generator in that direction. Accordingly, a more efficient construction of drive shaft may be selected for use.
Preferably, the generator system comprises a permanent magnet generator.
Preferably, the drive shaft is operable to bend as a result of a misalignment between said rotor and said generator system.
A further advantage of the system is presented in situations wherein a misalignment exists between the wind turbine rotor and the generator system, e.g. as a result of faulty construction procedures and/or mounting of wind turbine components. In such a case, the flexible shaft may be operable to bend and accommodate misalignments in the wind turbine construction.
Preferably, said drive shaft comprises at least one continuous unsupported section, said shaft arranged such that said unsupported section is operable to bend relative to said rotor and said generator system.
Description of the Drawing An embodiment of the invention will now be described, by way of example only, with reference to the accompanying drawings, in which:
Preferably, the drive shaft comprises a composite fibre shaft, wherein substantially all of the fibres are oriented in a parallel winding direction. Preferably, at least 50% to 95% of the fibres are oriented in a parallel winding direction.
As the fibres are oriented in the same direction, the torsional strength will be concen-trated in that direction. As in wind turbines the drive shaft will only rotate in one di-rection, consequently substantially all of the torque will only ever be transferred to the generator in that direction. Accordingly, a more efficient construction of drive shaft may be selected for use.
Preferably, the generator system comprises a permanent magnet generator.
Preferably, the drive shaft is operable to bend as a result of a misalignment between said rotor and said generator system.
A further advantage of the system is presented in situations wherein a misalignment exists between the wind turbine rotor and the generator system, e.g. as a result of faulty construction procedures and/or mounting of wind turbine components. In such a case, the flexible shaft may be operable to bend and accommodate misalignments in the wind turbine construction.
Preferably, said drive shaft comprises at least one continuous unsupported section, said shaft arranged such that said unsupported section is operable to bend relative to said rotor and said generator system.
Description of the Drawing An embodiment of the invention will now be described, by way of example only, with reference to the accompanying drawings, in which:
8 Fig. 1 is a cross-sectional view of a wind turbine according to a first embodi-ment of the invention, Fig. 2 is a cross-sectional view of a wind turbine according to a second em-bodiment of the invention, Fig. 3 is a perspective view of a drive shaft coupling mechanism for use in an embodiment of the invention, and Fig. 4 is an enlarged cross-sectional view of the drive shaft coupling mecha-nism of Fig. 3.
Detailed Description of the Invention With reference to Fig. 1, a wind turbine according to a first embodiment of the inven-tion is indicated generally at 10. The wind turbine 10 comprises a tower 12 and a tur-bine main frame 14, the main frame 14 provided at the upper end of said tower having a windward side 14a and an opposed leeward side 14b. First and second through-going apertures 16a,16b are defined in the windward side 14a and the op-posed leeward side 14b respectively, said apertures 16a,16b in line with each other, to allow a shaft to extend through said main frame 14 from said windward side 14a to said leeward side 14b. The main frame 14 is adapted to swivel on top of the tower12 to correct the yaw angle of the wind turbine 10, so that the turbine is continually facing the wind direction.
A support shaft 18 is provided at said windward side 14a of said main frame 14, rig-idly mounted to the external surface of said main frame 14. The support shaft 18 com-prises a cylindrical tubular body which is positioned about said first aperture 16a, con-centric to said aperture 16a. In Fig. 1, the support shaft 18 is shown as bolted to the main frame 14 using bolts 19, but it will be understood that any suitable attachment method may be used to secure the support shaft 18 to the main frame 14.
Preferably, the support shaft 18 is releasably mounted to the main frame 14, to allow for removal of the support shaft 18 from the wind turbine 10, e.g. for servicing and maintenance purposes.
Detailed Description of the Invention With reference to Fig. 1, a wind turbine according to a first embodiment of the inven-tion is indicated generally at 10. The wind turbine 10 comprises a tower 12 and a tur-bine main frame 14, the main frame 14 provided at the upper end of said tower having a windward side 14a and an opposed leeward side 14b. First and second through-going apertures 16a,16b are defined in the windward side 14a and the op-posed leeward side 14b respectively, said apertures 16a,16b in line with each other, to allow a shaft to extend through said main frame 14 from said windward side 14a to said leeward side 14b. The main frame 14 is adapted to swivel on top of the tower12 to correct the yaw angle of the wind turbine 10, so that the turbine is continually facing the wind direction.
A support shaft 18 is provided at said windward side 14a of said main frame 14, rig-idly mounted to the external surface of said main frame 14. The support shaft 18 com-prises a cylindrical tubular body which is positioned about said first aperture 16a, con-centric to said aperture 16a. In Fig. 1, the support shaft 18 is shown as bolted to the main frame 14 using bolts 19, but it will be understood that any suitable attachment method may be used to secure the support shaft 18 to the main frame 14.
Preferably, the support shaft 18 is releasably mounted to the main frame 14, to allow for removal of the support shaft 18 from the wind turbine 10, e.g. for servicing and maintenance purposes.
9 The wind turbine 10 further comprises a rotor, indicated generally at 20, having a plu-rality of rotor blades (not shown) mounted thereon. The rotor 20 comprises a rotor hub 22 having a front flange 24 and a collar 26 depending from a turbine side 24a of said flange 24.
The rotor 20 is provided on the wind turbine 10 by mounting the rotor hub 22 to the support shaft 18. The collar 26 fits about the support shaft 18, with two sets of bear-ings 28a,28b provided between the support shaft 18 and the collar 26, the bearings 28a,28b allowing the rotation of the rotor hub 22 about the support shaft 18.
With this - construction, the structural load or weight of the rotor 20 is transferred to the structure of the wind turbine 10 from the support shaft 18 to the main frame 14. The rotor hub 22 is directly mounted to the support shaft 18, i.e. there are no vibration damping ele-ments used between the rotor 20 and the support shaft 18.
It will be understood that while two sets of bearings 28a,28b are shown in the em-bodiment of Fig. I, any suitable number or arrangement of bearings may be used which are operable to support the weight of the rotor 20 while allowing rotation of the rotor hub 22 about the support shaft 18.
While in the rotor hub 22 of Fig. 1, the collar 26 is shown as being bolted to the front flange 24 of the rotor hub 22 using bolts 27, it will be understood that any suitable hub construction may be used, e.g. a single cast-iron structure.
A turbine drive shaft 30 extends from a first end 30a rigidly connected to said turbine side 24a of said front flange 24, the drive shaft 30 extending through said support shaft 18 into the interior of said main frame 14 towards the opposed leeward side 14b of the main frame 14 to a second end 30b. The drive shaft 30 is chosen to be mechanically anisotropic, i.e. the shaft has different mechanical properties in different directions. In particular, the drive shaft 30 is chosen to be flexible with regard to bending moments, and high in torsional strength. Due to the wind turbine construction, the drive shaft 30 is only required to transfer torque from the rotor 20 to a generator of the wind turbine ¨ the drive shaft 30 does not carry any of the structural load of the rotor 20. Accord-ingly, no shaft bearings or rollers are required in the illustrated construction.
Preferably, a composite shaft is used, which is manufactured with the aim of produc-ing a shaft which is flexible in bending while being strong in torsion.
Examples of suitable composite shafts include a filament winding-type shaft, a pre-preg fibre shaft 5 (i.e. a "pre-impregnated" composite fibre shaft), a slatted construction-type shaft (wherein the shaft is formed by a plurality of slats arranged in, for example, a longitu-dinal or helical manner, the slats forming a tubular shaft, adjacent slats coupled to one another using a suitable flexible adhesive).
The rotor 20 is provided on the wind turbine 10 by mounting the rotor hub 22 to the support shaft 18. The collar 26 fits about the support shaft 18, with two sets of bear-ings 28a,28b provided between the support shaft 18 and the collar 26, the bearings 28a,28b allowing the rotation of the rotor hub 22 about the support shaft 18.
With this - construction, the structural load or weight of the rotor 20 is transferred to the structure of the wind turbine 10 from the support shaft 18 to the main frame 14. The rotor hub 22 is directly mounted to the support shaft 18, i.e. there are no vibration damping ele-ments used between the rotor 20 and the support shaft 18.
It will be understood that while two sets of bearings 28a,28b are shown in the em-bodiment of Fig. I, any suitable number or arrangement of bearings may be used which are operable to support the weight of the rotor 20 while allowing rotation of the rotor hub 22 about the support shaft 18.
While in the rotor hub 22 of Fig. 1, the collar 26 is shown as being bolted to the front flange 24 of the rotor hub 22 using bolts 27, it will be understood that any suitable hub construction may be used, e.g. a single cast-iron structure.
A turbine drive shaft 30 extends from a first end 30a rigidly connected to said turbine side 24a of said front flange 24, the drive shaft 30 extending through said support shaft 18 into the interior of said main frame 14 towards the opposed leeward side 14b of the main frame 14 to a second end 30b. The drive shaft 30 is chosen to be mechanically anisotropic, i.e. the shaft has different mechanical properties in different directions. In particular, the drive shaft 30 is chosen to be flexible with regard to bending moments, and high in torsional strength. Due to the wind turbine construction, the drive shaft 30 is only required to transfer torque from the rotor 20 to a generator of the wind turbine ¨ the drive shaft 30 does not carry any of the structural load of the rotor 20. Accord-ingly, no shaft bearings or rollers are required in the illustrated construction.
Preferably, a composite shaft is used, which is manufactured with the aim of produc-ing a shaft which is flexible in bending while being strong in torsion.
Examples of suitable composite shafts include a filament winding-type shaft, a pre-preg fibre shaft 5 (i.e. a "pre-impregnated" composite fibre shaft), a slatted construction-type shaft (wherein the shaft is formed by a plurality of slats arranged in, for example, a longitu-dinal or helical manner, the slats forming a tubular shaft, adjacent slats coupled to one another using a suitable flexible adhesive).
10 As the drive shaft 30 is flexible to bending moments, this allows the shaft 30 to sub-stantially prevent the transmission of any bending forces from the rotor 20 to any gen-erator components (for example, as a result of misaligned or moving shaft ends), con-sequently reducing the wear-and-tear of such components.
The wind turbine 10 further comprises a generator indicated generally at 32 provided at the leeward side 14b of the main frame 14. The generator 32 comprises a generator housing 34, a generator stator 36 affixed to said housing 34, and a generator rotor 38 provided in said housing 34. The generator rotor 38 is mounted to an extension 53 of the drive shaft 30. This extended shaft 53 is supported via bearings 40 in said genera-tor housing 34, such that said generator rotor 38 is operable to rotate within said hous-ing 34. Rotation of the generator rotor 38 relative to the generator stator 36 results in the generation of electrical power in the generator 32. It will be understood that the wind turbine 10 may comprise any suitable connection mechanism coupled with the generator 32 such that the generated power may be transmitted to the power grid.
Other generator configurations can be foreseen, for example, the drive shaft 30 may extend through the main frame 14 past the leeward side 14b of the main frame 14. In such a construction, the generator rotor 38 may be directly mounted to the drive shaft 30.
The generator 32 is provided at the leeward side 14b of said main frame 14, the gen-erator 32 further comprising a generator coupling 42 connected to said generator rotor 38, the generator coupling 42 extending into the interior of the main frame via said
The wind turbine 10 further comprises a generator indicated generally at 32 provided at the leeward side 14b of the main frame 14. The generator 32 comprises a generator housing 34, a generator stator 36 affixed to said housing 34, and a generator rotor 38 provided in said housing 34. The generator rotor 38 is mounted to an extension 53 of the drive shaft 30. This extended shaft 53 is supported via bearings 40 in said genera-tor housing 34, such that said generator rotor 38 is operable to rotate within said hous-ing 34. Rotation of the generator rotor 38 relative to the generator stator 36 results in the generation of electrical power in the generator 32. It will be understood that the wind turbine 10 may comprise any suitable connection mechanism coupled with the generator 32 such that the generated power may be transmitted to the power grid.
Other generator configurations can be foreseen, for example, the drive shaft 30 may extend through the main frame 14 past the leeward side 14b of the main frame 14. In such a construction, the generator rotor 38 may be directly mounted to the drive shaft 30.
The generator 32 is provided at the leeward side 14b of said main frame 14, the gen-erator 32 further comprising a generator coupling 42 connected to said generator rotor 38, the generator coupling 42 extending into the interior of the main frame via said
11 second aperture 16b. The second end 30b of said drive shaft 30 is connected to said generator coupling 42. Accordingly, the drive shaft 30 is directly connected to the generator rotor 38, resulting in a direct-drive machine.
Preferably, the generator 32 is releasably mounted to the wind turbine main frame 14.
In Fig. 1, the generator housing 34 is coupled to the leeward side 14b of the main frame 14 using bolts 44. It will be understood that any suitable coupling may be used to secure the generator 32 to the main frame 14.
As the rotor support construction of the wind turbine 10 means that the structural load of the rotor 20 is supported by the main frame 14 and tower 12 of the turbine 10 itself, and as the drive shaft 30 is flexible enough to substantially prevent the transmission of bending moments from the rotor hub 22 to the generator 32, accordingly there are sub-stantially no reaction forces acting on the generator 32 apart from the torque transmit-ted by the drive shaft 30. The absence of reaction forces removes the need for the gen-erator 32 to be load-balanced when installed in the turbine 10, and accordingly the generator 32 can be rigidly mounted to the main frame 14, i.e. without requiring the use of vibration damping elements.
As no vibration damping elements are used in the construction, therefore damper fail-ure is no longer an issue in turbine design, and the performance of turbine components can be more accurately modelled at the design stage. The effects of wear-and-tear can be better predicted for the turbine components, and as a result, more reliable, more efficient and better modelled components can be employed at those locations subject to the most stresses and strains, e.g. hub rotor bearings 28a,28b, generator bearings 40.
As the generator 32 is not subject to substantial reaction forces, the reliability of the generator 32 is increased as a constant air gap can be reliably maintained between the generator stator 36 and the generator rotor 38. Furthermore, as the generator 32 does not have to be load-balanced with regard to the forces due to the structural load of the rotor 20, the installation operation of a generator 32 in the turbine 10 is made substan-tially easier. Accordingly, preferably the generator 32 is provided as a single modular construction, which is easily mounted to the wind turbine main frame 14. This pro-
Preferably, the generator 32 is releasably mounted to the wind turbine main frame 14.
In Fig. 1, the generator housing 34 is coupled to the leeward side 14b of the main frame 14 using bolts 44. It will be understood that any suitable coupling may be used to secure the generator 32 to the main frame 14.
As the rotor support construction of the wind turbine 10 means that the structural load of the rotor 20 is supported by the main frame 14 and tower 12 of the turbine 10 itself, and as the drive shaft 30 is flexible enough to substantially prevent the transmission of bending moments from the rotor hub 22 to the generator 32, accordingly there are sub-stantially no reaction forces acting on the generator 32 apart from the torque transmit-ted by the drive shaft 30. The absence of reaction forces removes the need for the gen-erator 32 to be load-balanced when installed in the turbine 10, and accordingly the generator 32 can be rigidly mounted to the main frame 14, i.e. without requiring the use of vibration damping elements.
As no vibration damping elements are used in the construction, therefore damper fail-ure is no longer an issue in turbine design, and the performance of turbine components can be more accurately modelled at the design stage. The effects of wear-and-tear can be better predicted for the turbine components, and as a result, more reliable, more efficient and better modelled components can be employed at those locations subject to the most stresses and strains, e.g. hub rotor bearings 28a,28b, generator bearings 40.
As the generator 32 is not subject to substantial reaction forces, the reliability of the generator 32 is increased as a constant air gap can be reliably maintained between the generator stator 36 and the generator rotor 38. Furthermore, as the generator 32 does not have to be load-balanced with regard to the forces due to the structural load of the rotor 20, the installation operation of a generator 32 in the turbine 10 is made substan-tially easier. Accordingly, preferably the generator 32 is provided as a single modular construction, which is easily mounted to the wind turbine main frame 14. This pro-
12 vides for easier installation and removal of a generator 32 to the wind turbine 10 with-out a relatively complicated load-balancing operation, and the replacement of an exist-ing generator 32 with a new generator (e.g. for upgrade purposes) is made considera-bly more straightforward, and results in reduced down-time for the wind turbine 10 overall.
Similarly, the rotor 20 may also be provided as a singular modular construction, which can be relatively easily decoupled from the wind turbine main frame 14 for servicing and/or replacement.
With reference to Fig. 2, a second embodiment of a wind turbine according to the in-vention is indicated generally at 11. For the sake of brevity, components similar to those described in the first embodiment are indicated using the same reference numer-als, and the relevant sections of the above description can apply to the embodiment of Fig. 2.
In the embodiment of Fig. 2, the wind turbine 11 further comprises a gearbox 46 hav-ing an input coupling 48 and an output coupling 50, the gearbox 46 rigidly mounted to the main frame 14 via base 47. The drive shaft 30 is directly connected to the gearbox 46 using input coupling 48, while the gearbox 46 is coupled to the generator 32 using a secondary shaft 52, the secondary shaft 52 extending between a gearbox output cou-pling 50 and the generator coupling 42. It will be understood that the secondary shaft 52 may be flexible in bending moments similar to the drive shaft 30, to prevent the transmission of any bending moments between the gearbox 46 and the generator 32.
Similar to the generator 32 as described in the first embodiment, as the drive shaft 30 is adapted to prevent transmission of bending moments from the rotor hub 22 to the gearbox 46, the gearbox does not have to be load-balanced with respect to the rotor hub 22. Accordingly, the gearbox 46 can be rigidly mounted to the main frame 14.
Preferably, the gearbox 46 is releasably mounted to the main frame 14, allowing for relatively easy removal of the gearbox 46 from the wind turbine 11 for servicing and/or replacement.
Similarly, the rotor 20 may also be provided as a singular modular construction, which can be relatively easily decoupled from the wind turbine main frame 14 for servicing and/or replacement.
With reference to Fig. 2, a second embodiment of a wind turbine according to the in-vention is indicated generally at 11. For the sake of brevity, components similar to those described in the first embodiment are indicated using the same reference numer-als, and the relevant sections of the above description can apply to the embodiment of Fig. 2.
In the embodiment of Fig. 2, the wind turbine 11 further comprises a gearbox 46 hav-ing an input coupling 48 and an output coupling 50, the gearbox 46 rigidly mounted to the main frame 14 via base 47. The drive shaft 30 is directly connected to the gearbox 46 using input coupling 48, while the gearbox 46 is coupled to the generator 32 using a secondary shaft 52, the secondary shaft 52 extending between a gearbox output cou-pling 50 and the generator coupling 42. It will be understood that the secondary shaft 52 may be flexible in bending moments similar to the drive shaft 30, to prevent the transmission of any bending moments between the gearbox 46 and the generator 32.
Similar to the generator 32 as described in the first embodiment, as the drive shaft 30 is adapted to prevent transmission of bending moments from the rotor hub 22 to the gearbox 46, the gearbox does not have to be load-balanced with respect to the rotor hub 22. Accordingly, the gearbox 46 can be rigidly mounted to the main frame 14.
Preferably, the gearbox 46 is releasably mounted to the main frame 14, allowing for relatively easy removal of the gearbox 46 from the wind turbine 11 for servicing and/or replacement.
13 The main frame 14 of Fig. 1 and 2 is shown as a substantially enclosed structure, but it will be understood that other suitable constructions may be employed, e.g. an open-sided cradle construction, allowing relatively easy access to the contained components.
It will be understood that while the drive shaft 30 is shown as a hollow tubular con-struction any suitable shaft type may be used. The thickness of the wall of the drive shaft 30 preferably may be selected as less than 10 mm, 20mm, 30mm, 40mm, etc.
up to 400mm thickness. It will further be understood that the drive shaft 30 may comprise any suitable nanocomposite material, e.g. nano clay, carbon nanotubes, nano silica etc.
Preferably, the drive shaft 30 comprises-an electrically insulating material ¨
this would prevent the transmission of high levels electricity to components of the wind turbine which may be experienced in the event of a lightening strike. It will be understood that the drive shaft 30 may be chosen of any suitable length, e.g. more than 0.1m, lm, 3m, 5m. 7m, 9m, Jim, etc. in length.
It will be understood that the present invention is suitable for use in any suitable wind turbine construction, e.g. turbines having a maximum power rating of above 2MW, 3MW, 4MW, up to and above 35 MW, etc. Preferably, the system is used in variable speed turbines.
With reference to Figs. 3 and 4, a sample drive shaft coupling method according to an embodiment of the invention is illustrated for a sample drive shaft 300.
The drive shaft 300 comprises a substantially cylindrical hollow body 301 having a first end 300a and a second end 300b. The first and second ends 300a,300b are flared outwardly from the centreline of the shaft, providing flared sections 302,304 of in-creasing diameter located respectively at said first and second ends 300a,300b.
The drive shaft 300 further comprises first and second coupling flanges 308,310. Said first coupling flange 308 is provided at said first end 300a of said shaft 300, and said second coupling flange 310 is provided at said second end 300b of said shaft 300. The first and second coupling flanges 308,310 comprise circular bolting collars 308a,310a
It will be understood that while the drive shaft 30 is shown as a hollow tubular con-struction any suitable shaft type may be used. The thickness of the wall of the drive shaft 30 preferably may be selected as less than 10 mm, 20mm, 30mm, 40mm, etc.
up to 400mm thickness. It will further be understood that the drive shaft 30 may comprise any suitable nanocomposite material, e.g. nano clay, carbon nanotubes, nano silica etc.
Preferably, the drive shaft 30 comprises-an electrically insulating material ¨
this would prevent the transmission of high levels electricity to components of the wind turbine which may be experienced in the event of a lightening strike. It will be understood that the drive shaft 30 may be chosen of any suitable length, e.g. more than 0.1m, lm, 3m, 5m. 7m, 9m, Jim, etc. in length.
It will be understood that the present invention is suitable for use in any suitable wind turbine construction, e.g. turbines having a maximum power rating of above 2MW, 3MW, 4MW, up to and above 35 MW, etc. Preferably, the system is used in variable speed turbines.
With reference to Figs. 3 and 4, a sample drive shaft coupling method according to an embodiment of the invention is illustrated for a sample drive shaft 300.
The drive shaft 300 comprises a substantially cylindrical hollow body 301 having a first end 300a and a second end 300b. The first and second ends 300a,300b are flared outwardly from the centreline of the shaft, providing flared sections 302,304 of in-creasing diameter located respectively at said first and second ends 300a,300b.
The drive shaft 300 further comprises first and second coupling flanges 308,310. Said first coupling flange 308 is provided at said first end 300a of said shaft 300, and said second coupling flange 310 is provided at said second end 300b of said shaft 300. The first and second coupling flanges 308,310 comprise circular bolting collars 308a,310a
14 which may be bolted to suitable wind turbine components, e.g. a wind turbine rotor hub, a generator rotor, a gearbox for connection to a generator system, etc.
The first and second coupling flanges 308,310 further comprise first and second frus-toconical projections 312,314 (seen in outline in Fig. 3) provided respectively on said first and second flanges 308,310. Said frustoconical projections 312,314 are received within the respective first and second flared sections 302,304 of the shaft body 301. A
series of apertures are defined on said first and second frustoconical projections 312,314, said apertures arranged to receive a series of pins 306. Said pins 306 project from the surface of said frustoconical projections 312,314 away from the central axis of the shaft 300, and are received within the shaft body 301 at said flared sections 302,304. (This arrangement can be seen in more detail in the enlarged cross-sectional view of Fig. 4, which shows a portion of the first frustoconical projection 312 received within the first flared section 302.) In a preferred embodiment, the main shaft body 301 is formed from a fibre-based ma-terial, with the first and second coupling flanges 308,310 formed from a resilient mate-rial, e.g. a metal such as steel, which is more suitable for bolting to wind turbine com-ponents than the fibre-based main shaft body 301. In a first embodiment, the fibre-based main shaft may be constructed as a standard shaft body, having flared ends cor-responding to flared sections 302,304. Holes are then formed in the flared ends, corre-sponding to the apertures provided on the frustocontical projections of the coupling flanges, e.g. by drilling holes in the flared ends of the shaft body. The series of pins may then be inserted in the holes in the flared ends to extend through to the apertures in the coupling flanges, to secure the coupling flanges to the main shaft body.
In a preferred construction of such a fibre-based main shaft, the main body 301 of the shaft is processed as a standard fibre-wound construction, with the coupling flanges 308,310 provided with said series of pins 306 projecting from the surface of said frus-toconical projections 312,314, positioned at either end of the projected shaft body.
When the fibres being currently wound to form the shaft body 301 reach one of the ends 300a,300b of the shaft body and the particular coupling flange 308,310 to be po-sitioned at said end, the current fibres are applied to the surface of the frustoconical projection 312,314 of the flange 308,310 in question, with a plurality of the fibres wound around or intertwined with said pins 306 on the surface of said projection 312,314, in order to provide for an equal distribution of forces from the coupling flanges to the shaft body, to improve the retention of the pins 306 within the shaft300, 5 and to improve the coupling between the shaft body 301 and the coupling flanges 308,310. This embodiment of winding the fibres around the pins is also preferred as it prevents damage to the fibres of the shaft which may be caused by drilling holes in the flared sections of the shaft body.
10 The drive shaft 30,300 may be manufactured using any suitable manufacturing method or technique, e.g. Vacuum Assisted Resin Transfer Moulding (VARTM), hand lay-up, injection moulding, Resin Transfer Moulding (RTM), spray lay-up, etc.
One particular method of construction may be employed in order to manufacture a
The first and second coupling flanges 308,310 further comprise first and second frus-toconical projections 312,314 (seen in outline in Fig. 3) provided respectively on said first and second flanges 308,310. Said frustoconical projections 312,314 are received within the respective first and second flared sections 302,304 of the shaft body 301. A
series of apertures are defined on said first and second frustoconical projections 312,314, said apertures arranged to receive a series of pins 306. Said pins 306 project from the surface of said frustoconical projections 312,314 away from the central axis of the shaft 300, and are received within the shaft body 301 at said flared sections 302,304. (This arrangement can be seen in more detail in the enlarged cross-sectional view of Fig. 4, which shows a portion of the first frustoconical projection 312 received within the first flared section 302.) In a preferred embodiment, the main shaft body 301 is formed from a fibre-based ma-terial, with the first and second coupling flanges 308,310 formed from a resilient mate-rial, e.g. a metal such as steel, which is more suitable for bolting to wind turbine com-ponents than the fibre-based main shaft body 301. In a first embodiment, the fibre-based main shaft may be constructed as a standard shaft body, having flared ends cor-responding to flared sections 302,304. Holes are then formed in the flared ends, corre-sponding to the apertures provided on the frustocontical projections of the coupling flanges, e.g. by drilling holes in the flared ends of the shaft body. The series of pins may then be inserted in the holes in the flared ends to extend through to the apertures in the coupling flanges, to secure the coupling flanges to the main shaft body.
In a preferred construction of such a fibre-based main shaft, the main body 301 of the shaft is processed as a standard fibre-wound construction, with the coupling flanges 308,310 provided with said series of pins 306 projecting from the surface of said frus-toconical projections 312,314, positioned at either end of the projected shaft body.
When the fibres being currently wound to form the shaft body 301 reach one of the ends 300a,300b of the shaft body and the particular coupling flange 308,310 to be po-sitioned at said end, the current fibres are applied to the surface of the frustoconical projection 312,314 of the flange 308,310 in question, with a plurality of the fibres wound around or intertwined with said pins 306 on the surface of said projection 312,314, in order to provide for an equal distribution of forces from the coupling flanges to the shaft body, to improve the retention of the pins 306 within the shaft300, 5 and to improve the coupling between the shaft body 301 and the coupling flanges 308,310. This embodiment of winding the fibres around the pins is also preferred as it prevents damage to the fibres of the shaft which may be caused by drilling holes in the flared sections of the shaft body.
10 The drive shaft 30,300 may be manufactured using any suitable manufacturing method or technique, e.g. Vacuum Assisted Resin Transfer Moulding (VARTM), hand lay-up, injection moulding, Resin Transfer Moulding (RTM), spray lay-up, etc.
One particular method of construction may be employed in order to manufacture a
15 composite fibre shaft having a majority of fibres lying in the same direction, namely utilising fibres applied to a rotating mandrel to form a hollow shaft. In such a system, a mandrel is rotating in a particular direction (e.g. clockwise), while a jig running adja-cent the mandrel and along the length of the mandrel applies fibres to the surface of the rotating mandrel, the fibres being applied at an angle to the centreline of the man-drel (e.g. 450 to the normal). The jig runs back-and-forth along the length of the man-drel, resulting in successive layers of fibres building up on the mandrel, resulting in a cross-hatch style arrangement of fibres along the body of the mandrel. The fibres are treated in position to form a hollow shaft.
It will be foreseen that the drive shaft 30,300 may be of any suitable construction, for example, a hollow composite shaft having a thin-walled steel inner tube. The presence of the steel inner tube helps to prevent delamination and buckling of the shaft.
ln the proposed new method of manufacture, during the fibre application stage, the jig applies a first layer of fibres at a first angle a to the normal. After the jig reaches the end of the mandrel on the first pass, the direction of rotation of the mandrel is reversed (e.g. the rotation direction of the mandrel changes from clockwise to anti-clockwise), and the jig turns and travels in the reverse direction along the body of the mandrel.
It will be foreseen that the drive shaft 30,300 may be of any suitable construction, for example, a hollow composite shaft having a thin-walled steel inner tube. The presence of the steel inner tube helps to prevent delamination and buckling of the shaft.
ln the proposed new method of manufacture, during the fibre application stage, the jig applies a first layer of fibres at a first angle a to the normal. After the jig reaches the end of the mandrel on the first pass, the direction of rotation of the mandrel is reversed (e.g. the rotation direction of the mandrel changes from clockwise to anti-clockwise), and the jig turns and travels in the reverse direction along the body of the mandrel.
16 This results in the second layer of fibres being applied substantially in the same direc-tion as the fibres of the first layer, at an angle a to the normal, as opposed to the cross-hatch application of successive fibre layers provided by the known approach.
It will be understood that the fibres may be applied as successive layers of fibre-based material, wherein successive layers have a relative adhesive attraction to each other and to the underlying mandrel. Such a relative adhesion is sufficient to temporarily hold the fibre layers in position during application to the mandrel, such that the ap-plied layers will not unwind from the mandrel as the direction of rotation of the man-drel is reversed.
As soon as the jig returns to the start of the mandrel, it turns and resumes in a forward direction along the mandrel, and the direction of rotation of the mandrel is restored to the original direction (e.g. returning to clockwise rotation). The action of reversing the direction of rotation of the mandrel may be accomplished simply by reversing the po-larity of the motor rotating the mandrel once the jig reaches the end of the mandrel.
This procedure can be repeated for as many passes of the jig along the mandrel as re-quired, and consequently for as many layers of fibres as required. As a result, the fi-bres applied from the jig to the mandrel will all be lying in substantially the same di-rection along the body of the mandrel, at substantially the same angle a to the normal.
A shaft formed having such fibres in parallel alignment will have a high torsional strength in one direction. As the drive shaft of a wind turbine is mainly in general only required to transmit torque in one direction, this results in a drive shaft for a wind tur-bine having a greater torsional strength for same amount of fibres used in the construc-tion of the shaft, and consequently lower weight shafts may be produced having the same torque rating as currently-used standard shafts.
Preferably, the drive shaft would comprise a composite fibre shaft having a majority of fibres lying in the same direction along the body of the shaft, preferably at least 50 to 95% of fibres.
It will be understood that the fibres may be applied as successive layers of fibre-based material, wherein successive layers have a relative adhesive attraction to each other and to the underlying mandrel. Such a relative adhesion is sufficient to temporarily hold the fibre layers in position during application to the mandrel, such that the ap-plied layers will not unwind from the mandrel as the direction of rotation of the man-drel is reversed.
As soon as the jig returns to the start of the mandrel, it turns and resumes in a forward direction along the mandrel, and the direction of rotation of the mandrel is restored to the original direction (e.g. returning to clockwise rotation). The action of reversing the direction of rotation of the mandrel may be accomplished simply by reversing the po-larity of the motor rotating the mandrel once the jig reaches the end of the mandrel.
This procedure can be repeated for as many passes of the jig along the mandrel as re-quired, and consequently for as many layers of fibres as required. As a result, the fi-bres applied from the jig to the mandrel will all be lying in substantially the same di-rection along the body of the mandrel, at substantially the same angle a to the normal.
A shaft formed having such fibres in parallel alignment will have a high torsional strength in one direction. As the drive shaft of a wind turbine is mainly in general only required to transmit torque in one direction, this results in a drive shaft for a wind tur-bine having a greater torsional strength for same amount of fibres used in the construc-tion of the shaft, and consequently lower weight shafts may be produced having the same torque rating as currently-used standard shafts.
Preferably, the drive shaft would comprise a composite fibre shaft having a majority of fibres lying in the same direction along the body of the shaft, preferably at least 50 to 95% of fibres.
17 It will be understood that the generator 32 used in the design may be a permanent magnet generator (PMG), a synchronous generator, an asynchronous generator, a dou-bly-fed generator, etc.
The drive shaft 30,300 may be selected to have a maximum torsion capability, in that the shaft may break if the torsion acting on the shaft exceeds a defined level. This acts to protect the components of the generator 32 and/or gearbox 46 from any damage that might be incurred in the event of a sudden large increase in torque, e.g. a sudden gale force wind acting on the turbine rotor.
The drive shaft 30,300 may also be configured to be rated for a certain torsional vibra-tion frequency, and to dampen and torsional vibrations above such a frequency.
The ability to dampen high-frequency torsional vibrations allows for the system to reduce the effect of cocking or cogging torque. Cogging torque of electrical motors is the torque due to the interaction between the permanent magnets of the rotor and the stator slots of a Permanent Magnet (PM) machine, and can result in high-frequency "jerky"
torque. As the drive shaft 30,300 can dampen these high-frequency torsional vibra-tions, it prevents the transmission of this "jerkiness" to the rotor 20 and the turbine blades, which would normally result in acoustic noise emission from the turbine.
It will be understood that the use of the term "rigidly mounted" means that the compo-nents are mounted without damping elements, It will be understood that the use of the term "rigidly connected" means that compo-nents are directly connected or mounted together, e.g. without damping elements and/or without relative motion between the connected components.
As the shaft used is flexible to absorb the transmission of vibrations between the rotor and the generator system, such rigid mounting and connecting of components can be accomplished, eliminating the need for vibration damping elements in the wind tur-bine construction.
The drive shaft 30,300 may be selected to have a maximum torsion capability, in that the shaft may break if the torsion acting on the shaft exceeds a defined level. This acts to protect the components of the generator 32 and/or gearbox 46 from any damage that might be incurred in the event of a sudden large increase in torque, e.g. a sudden gale force wind acting on the turbine rotor.
The drive shaft 30,300 may also be configured to be rated for a certain torsional vibra-tion frequency, and to dampen and torsional vibrations above such a frequency.
The ability to dampen high-frequency torsional vibrations allows for the system to reduce the effect of cocking or cogging torque. Cogging torque of electrical motors is the torque due to the interaction between the permanent magnets of the rotor and the stator slots of a Permanent Magnet (PM) machine, and can result in high-frequency "jerky"
torque. As the drive shaft 30,300 can dampen these high-frequency torsional vibra-tions, it prevents the transmission of this "jerkiness" to the rotor 20 and the turbine blades, which would normally result in acoustic noise emission from the turbine.
It will be understood that the use of the term "rigidly mounted" means that the compo-nents are mounted without damping elements, It will be understood that the use of the term "rigidly connected" means that compo-nents are directly connected or mounted together, e.g. without damping elements and/or without relative motion between the connected components.
As the shaft used is flexible to absorb the transmission of vibrations between the rotor and the generator system, such rigid mounting and connecting of components can be accomplished, eliminating the need for vibration damping elements in the wind tur-bine construction.
18 The above describes a wind turbine construction which is of reduced weight, improved reliability, and can easily be serviced and upgraded. The invention is not limited to the embodiments described herein, and may be modified or adapted without departing from the scope of the present invention.
Claims (16)
1. A horizontal-axis wind turbine having a rotor with a diameter of at least 50 m length, the turbine comprising:
a wind turbine main frame;
a generator system comprising a generator that is rigidly mounted to said main frame without vibration damping elements;
a rotor hub, said hub mounted to a rigid support shaft provided on said main frame, wherein said hub is operable to rotate about said support shaft and wherein said support shaft transfers structural loading of said hub to said main frame; and a drive shaft rigidly connected to and extending from said hub, wherein said drive shaft is connected to said generator system to transfer torque from said hub to said generator system, wherein said drive shaft is a mechanically anisotropic shaft that has sufficient flexibility for preventing transmission of bending moments from the hub to the generator system by absorption of the bending moments;
wherein the drive shaft comprises a first coupling flange at its first end and a second coupling flange at an opposite end, the first coupling flange being bolted to said rotor hub and the second coupling flange being bolted to said generator system;
wherein the drive shaft is only supported at said first and second coupling flanges by said hub and said generator system, the drive shaft being free of shaft bearings and rollers at locations between the first and second ends.
a wind turbine main frame;
a generator system comprising a generator that is rigidly mounted to said main frame without vibration damping elements;
a rotor hub, said hub mounted to a rigid support shaft provided on said main frame, wherein said hub is operable to rotate about said support shaft and wherein said support shaft transfers structural loading of said hub to said main frame; and a drive shaft rigidly connected to and extending from said hub, wherein said drive shaft is connected to said generator system to transfer torque from said hub to said generator system, wherein said drive shaft is a mechanically anisotropic shaft that has sufficient flexibility for preventing transmission of bending moments from the hub to the generator system by absorption of the bending moments;
wherein the drive shaft comprises a first coupling flange at its first end and a second coupling flange at an opposite end, the first coupling flange being bolted to said rotor hub and the second coupling flange being bolted to said generator system;
wherein the drive shaft is only supported at said first and second coupling flanges by said hub and said generator system, the drive shaft being free of shaft bearings and rollers at locations between the first and second ends.
2. The wind turbine of claim 1, wherein said drive shaft is a composite material shaft.
3. The wind turbine of claim 2, wherein said drive shaft is selected from one of the following: a filament wound shaft, a pre-preg fiber composite shaft, a slatted-construction shaft.
4. The wind turbine of any one of claims 1 to 3, wherein said generator system comprises a gearbox coupled to a generator, said gearbox rigidly mounted to said main frame, wherein said drive shaft is directly connected to said gearbox to drive said generator.
5. The wind turbine of claim 4, wherein said generator is rigidly mounted to said main frame.
6. The wind turbine of any one of claims 1 to 5, wherein the rigid support shaft extends through the rotor hub and is connected to the hub at a most distal end of the hub, and wherein bearings are provided between an outer end of the rigid support shaft and an inner side of the hub.
7. The wind turbine of any one of claims 1 to 5, wherein said rigid support shaft is provided at a first end of said main frame, and wherein said generator system is releasably mounted to a second opposed end of said main frame.
8. The wind turbine of claim 7, wherein said generator system is releasably mounted to an exterior surface of said main frame.
9. The wind turbine of claim 7, wherein said rigid support shaft is releasably mounted to said first end of said main frame.
10. The wind turbine of any one of claims 1 to 9, wherein the wind turbine comprises at least two sets of hub bearings provided at said support shaft, said hub mounted to said sets of hub bearings.
11. The wind turbine of any one of claims 1 to 10, wherein said drive shaft is directly connected between said hub and said generator system.
12. The wind turbine of any one of claims 1 to 11, wherein said drive shaft comprises a fiber composite main shaft body.
13. The wind turbine of claim 12, wherein said at least one end of said fiber composite main shaft body is outwardly flared, and wherein at least one of said coupling flanges comprises a first substantially frustoconical projection, said first substantially frustoconical projection being received within said at least one outwardly flared end of said main shaft body.
14. The wind turbine of claim 13, wherein said drive shaft comprises a plurality of pins extending between said at least one flared end of said main shaft body and said first frustoconical projection of said at least one coupling flange, said plurality of pins retaining said at least one coupling flange within said at least one flared end of said main shaft body.
15. The wind turbine of claim 14, wherein the drive shaft is arranged such that a portion of fibers at said at least one flared end are wound around said plurality of pins to provide for an equal distribution of forces between said at least one coupling flange and said shaft body, and to improve the retention of said pins in the main shaft body.
16. A horizontal-axis wind turbine having a rotor with a diameter of at least 50 m length, the turbine comprising:
a wind turbine main frame;
a generator system at least a portion of which is rigidly mounted to said main frame;
a rotor hub, said hub mounted to a rigid support shaft provided on said main frame, wherein said hub is operable to rotate about said support shaft and wherein said support shaft transfers structural loading of said hub to said main frame; and a drive shaft rigidly connected to and extending from said hub, wherein said drive shaft is connected to said generator system to transfer torque from said hub to said generator system, wherein said drive shaft is a mechanically anisotropic shaft adapted to limit the bending moments transferred between said hub and said generator system, wherein said shaft comprises a fiber composite main shaft body and at least one coupling flange formed from a rigid material suitable for bolting, said at least one coupling flange being arranged to couple with at least one end of said main shaft body, wherein said at least one end of said fiber composite main shaft body is outwardly flared, and wherein said at least one coupling flange comprises a first substantially frustoconical projection, said first substantially frustoconical projection of said at least one coupling flange being received within said at least one outwardly flared end of said main shaft body.
a wind turbine main frame;
a generator system at least a portion of which is rigidly mounted to said main frame;
a rotor hub, said hub mounted to a rigid support shaft provided on said main frame, wherein said hub is operable to rotate about said support shaft and wherein said support shaft transfers structural loading of said hub to said main frame; and a drive shaft rigidly connected to and extending from said hub, wherein said drive shaft is connected to said generator system to transfer torque from said hub to said generator system, wherein said drive shaft is a mechanically anisotropic shaft adapted to limit the bending moments transferred between said hub and said generator system, wherein said shaft comprises a fiber composite main shaft body and at least one coupling flange formed from a rigid material suitable for bolting, said at least one coupling flange being arranged to couple with at least one end of said main shaft body, wherein said at least one end of said fiber composite main shaft body is outwardly flared, and wherein said at least one coupling flange comprises a first substantially frustoconical projection, said first substantially frustoconical projection of said at least one coupling flange being received within said at least one outwardly flared end of said main shaft body.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DKPA201070280 | 2010-06-21 | ||
| DKPA201070280 | 2010-06-21 |
Publications (2)
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| CA2743809A1 CA2743809A1 (en) | 2011-12-21 |
| CA2743809C true CA2743809C (en) | 2018-03-20 |
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| Application Number | Title | Priority Date | Filing Date |
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| CA2743809A Expired - Fee Related CA2743809C (en) | 2010-06-21 | 2011-06-21 | Flexible shaft wind turbine |
Country Status (5)
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|---|---|
| US (1) | US8664791B2 (en) |
| EP (1) | EP2397690A1 (en) |
| KR (1) | KR101775373B1 (en) |
| CN (1) | CN102297089B (en) |
| CA (1) | CA2743809C (en) |
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|---|---|---|---|---|
| EP2397309A1 (en) * | 2010-06-21 | 2011-12-21 | Envision Energy (Denmark) ApS | A Wind Turbine and a Shaft for a Wind Turbine |
| EP2593674B8 (en) * | 2010-07-12 | 2016-10-19 | ALSTOM Renewable Technologies | Wind turbine |
| DE102011075688A1 (en) * | 2011-05-11 | 2012-11-15 | SchäferRolls GmbH & Co. KG | Shaft assembly and method of making a shaft assembly |
| DE102012015357B4 (en) * | 2012-08-06 | 2018-05-17 | Centa-Antriebe Kirschey Gmbh | Non-shiftable clutch with torque monitoring |
| ES2585832T3 (en) | 2012-12-06 | 2016-10-10 | Nordex Energy Gmbh | Wind power installation |
| ES2550964T3 (en) | 2012-12-06 | 2015-11-13 | Nordex Energy Gmbh | Wind turbine |
| EP2740933B1 (en) | 2012-12-06 | 2015-07-29 | Nordex Energy GmbH | Wind energy system |
| GB201222971D0 (en) * | 2012-12-19 | 2013-01-30 | Romax Technology Ltd | Flexible driving shaft |
| JP6138633B2 (en) * | 2013-08-29 | 2017-05-31 | 株式会社日立製作所 | Wind power generation system |
| WO2015125153A2 (en) * | 2014-02-19 | 2015-08-27 | Valagam Rajagopal Raghunathan | A flexible torque transmitting means for wind turbine |
| CN106062360A (en) * | 2014-03-04 | 2016-10-26 | 纳巴风力公司 | Wind turbine drive train |
| KR101536755B1 (en) * | 2014-05-16 | 2015-07-16 | 한국고벨주식회사 | Integrated power transmission drive system for wind power plant |
| KR101626392B1 (en) | 2014-11-20 | 2016-06-02 | 대우조선해양 주식회사 | Wind turbine driving shaft having flexible flange |
| US9777764B2 (en) * | 2015-12-09 | 2017-10-03 | Hsiao-Lin Lee | Transmission shaft assembly |
| ES2824784T3 (en) * | 2016-12-29 | 2021-05-13 | Vestas Wind Sys As | Insulated shaft seal |
| WO2018141523A1 (en) * | 2017-02-03 | 2018-08-09 | Siemens Wind Power A/S | Wind turbine with a tubular support structure and a bearing assembly |
| US10961985B2 (en) | 2018-11-01 | 2021-03-30 | Vestas Wind Systems A/S | Wind turbine and methods including main shaft integrated with locking disc |
| EP3874147A1 (en) | 2018-11-01 | 2021-09-08 | Vestas Wind Systems A/S | Wind turbine with modular main shaft fastening system and rotor locking disc |
| WO2020088722A1 (en) | 2018-11-01 | 2020-05-07 | Vestas Wind Systems A/S | Wind turbine with rotor locking system |
| US11754035B2 (en) | 2021-04-12 | 2023-09-12 | Loubert S. Suddaby | Assembly for capturing oscillating fluid energy with hinged propeller and segmented driveshaft |
| CN113790206A (en) * | 2021-09-15 | 2021-12-14 | 上海涟屹轴承科技有限公司 | Composite material transmission shaft and sliding bearing thereof |
| KR102395640B1 (en) * | 2021-12-21 | 2022-05-09 | 양진이엔씨(주) | Lightweight wind power generator |
| CN114465443B (en) * | 2022-02-16 | 2023-12-22 | 东北大学 | Permanent magnet nonlinear energy trap for suppressing torsional vibration based on magnetic repulsion principle |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE2927955C2 (en) | 1979-07-11 | 1982-12-30 | Messerschmitt-Bölkow-Blohm GmbH, 8000 München | Method of manufacturing a coupling element |
| JPS63166519A (en) * | 1986-12-27 | 1988-07-09 | Hitachi Constr Mach Co Ltd | Rod-shaped object made of fiber reinforced resin |
| US4757211A (en) | 1987-07-10 | 1988-07-12 | Danregn Vidraft A/S | Machine for generating electricity |
| AU768212B2 (en) * | 1999-11-03 | 2003-12-04 | Vestas Wind Systems A/S | Method of controlling the operation of a wind turbine and wind turbine for use in said method |
| SE523196C2 (en) * | 2001-10-31 | 2004-03-30 | Saab Ab | Device and method of drive shaft |
| CN1280539C (en) | 2004-01-13 | 2006-10-18 | 张雪明 | Self-adaptive current power generation unit on seabed |
| FR2898935B1 (en) | 2006-03-27 | 2008-07-04 | Francois Guy Jacques Re Millet | DEVICE FOR ORIENTING DRILLING TOOLS |
| US7682256B2 (en) * | 2006-09-13 | 2010-03-23 | Kop-Flex Inc. | Flange design for filament wound composite shaft |
| WO2008124674A1 (en) * | 2007-04-06 | 2008-10-16 | Lawrie Technology, Inc. | High torque density flexible composite driveshaft |
| ES2723877T3 (en) * | 2007-11-15 | 2019-09-03 | Siemens Gamesa Renewable Energy Innovation & Technology SL | Method and system for the operation of a wind turbine |
| CN201177015Y (en) | 2008-01-22 | 2009-01-07 | 黄顺国 | Flexible coupler for wind-driven generator group |
| EP2397309A1 (en) * | 2010-06-21 | 2011-12-21 | Envision Energy (Denmark) ApS | A Wind Turbine and a Shaft for a Wind Turbine |
-
2011
- 2011-06-20 KR KR1020110059837A patent/KR101775373B1/en not_active Application Discontinuation
- 2011-06-20 EP EP11170527A patent/EP2397690A1/en not_active Withdrawn
- 2011-06-21 CA CA2743809A patent/CA2743809C/en not_active Expired - Fee Related
- 2011-06-21 US US13/164,917 patent/US8664791B2/en not_active Expired - Fee Related
- 2011-06-21 CN CN201110167094.8A patent/CN102297089B/en active Active
Also Published As
| Publication number | Publication date |
|---|---|
| US8664791B2 (en) | 2014-03-04 |
| EP2397690A1 (en) | 2011-12-21 |
| CN102297089A (en) | 2011-12-28 |
| US20110309631A1 (en) | 2011-12-22 |
| CN102297089B (en) | 2014-06-25 |
| KR20110139129A (en) | 2011-12-28 |
| KR101775373B1 (en) | 2017-09-06 |
| CA2743809A1 (en) | 2011-12-21 |
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Effective date: 20160620 |
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Effective date: 20200831 |